JP7533017B2 - Vehicle drive device - Google Patents

Description

The present invention relates to a vehicle drive device that includes a rotating electric machine having an input member that is drivingly connected to an internal combustion engine, a stator, and a rotor that is arranged radially inward of the stator and functions as a driving force source for wheels, a power transmission mechanism that transmits rotation transmitted from the rotating electric machine to the wheels, a rotor support member that supports the rotor, and a friction engagement device.

An example of such a vehicle drive device is disclosed in the following Patent Document 1. In the following explanation of this background art, the reference symbols in Patent Document 1 will be quoted in parentheses.

In the vehicle drive device (1) of Patent Document 1, the rotor support member (30) is formed in a cylindrical shape extending along the axial direction (L) and includes a cylindrical portion (31) that supports the rotor (Ro) from the inside (R1) in the radial direction (R), and a flange portion (35) that is formed to extend from the cylindrical portion (31) to the inside (R1) in the radial direction (R) and is disposed adjacent to one side (L2) in the axial direction (L) with respect to the first engagement device (CL1). In other words, the rotor support member (30) is formed in a cylindrical shape with a bottom that opens toward the other side (L1) in the axial direction (L). The first engagement device (CL1) and the second engagement device (CL2) as friction engagement devices are disposed on one side (L1) in the axial direction (L) with respect to the flange portion (35) and on the inside (R1) in the radial direction (R) with respect to the cylindrical portion (31).

WO 2017/057190 (Figure 3)

In the manufacturing process of the vehicle drive device (1) of Patent Document 1, the rotor (Ro), rotor support member (30), and friction engagement devices (CL1, CL2) are integrally assembled to produce a first assembly. The first assembly is then assembled to a second assembly that is separate from the first assembly. In general, the assembly work of the first assembly to the second assembly is performed while maintaining the posture of the first assembly so that the rotation axis (X) of the rotor (Ro) is aligned vertically. However, when some of the elements constituting the first assembly are assembled to be movable relative to the rotor support member (30) in the axial direction, the weight of the element may cause a part of the first assembly to fall off from the opening of the rotor support member (30). This requires measures such as attaching a jig to prevent the element from falling off, which complicates the manufacturing process.

Therefore, it is desirable to realize a vehicle drive device that has a structure that can prevent a part of a first assembly including a rotor, a rotor support member, and a friction engagement device from falling off through an opening in the rotor support member when the first assembly is assembled to a second assembly separate from the first assembly.

In view of the above, the characteristic configuration of the vehicle drive device is as follows:
an input member drivingly connected to the internal combustion engine;
a rotating electric machine having a stator and a rotor disposed radially inward of the stator and functioning as a driving force source for a wheel;
a power transmission mechanism that transmits rotation transmitted from the rotating electric machine to the wheels;
a rotor support member for supporting the rotor;
a first engagement device including a first friction plate and a second friction plate arranged side by side in the axial direction, and a first piston portion that presses the first friction plate and the second friction plate in the axial direction,
The first engagement device is disposed in a power transmission path between the input member and the rotating electric machine.
a first outer support member that supports the first friction plate from the outside in the radial direction;
A first inner support member that supports the second friction plate from the inside in the radial direction,
the first inner support member includes a cylindrical support portion that is formed in a cylindrical shape extending along the axial direction and supports the second friction plate, and a radially extending support portion that is formed so as to extend radially inward from the cylindrical support portion,
the radially extending support portion is coupled to the input member such that the input member and the first inner support member rotate together;
The first piston portion is disposed on a first axial side, which is one side in the axial direction, with respect to the radially extending support portion,
the rotor support member includes a cylindrical portion formed in a cylindrical shape extending along the axial direction and supporting the rotor from the inside in the radial direction, and a flange portion formed in a radially inner side relative to the cylindrical portion and extending along the radial direction and connected to the cylindrical portion,
The first engagement device is disposed on a first side in the axial direction with respect to the flange portion and on an inner side in the radial direction with respect to the cylindrical portion,
the first outer support member is configured to open toward the first axial side and rotate integrally with the cylindrical portion,
An annular member extending in a circumferential direction is fixed to an inner peripheral portion of the cylindrical portion,
The annular member is arranged on the first axial side relative to the first friction plate and the second friction plate, and is positioned so as to overlap with at least one of the first piston portion and the second friction plate when viewed axially along the axial direction.

According to this characteristic configuration, when a first assembly including a rotor, a rotor support member, and a first engagement device is assembled to a second assembly other than the first assembly, even if the first engagement device moves relative to the rotor support member toward the first axial side, at least one of the first piston portion and the second friction plate abuts against the annular member. This makes it possible to restrict the first friction plate of the first engagement device from moving relative to the opening on the first axial side of the rotor support member toward the first axial side. In other words, it is possible to restrict the first friction plate from coming off the rotor support member. Therefore, when a first assembly including a rotor, a rotor support member, and a first engagement device is assembled to a second assembly other than the first assembly, it is possible to restrict a part of the first assembly from falling off through the opening of the rotor support member.

FIG. 1 is a schematic diagram showing a schematic configuration of a vehicle drive device according to an embodiment; FIG. 1 is a partial cross-sectional view of a vehicle drive device according to an embodiment; FIG. 1 is a partially enlarged cross-sectional view of a vehicle drive device according to an embodiment; FIG. 1 is a partially enlarged cross-sectional view of a vehicle drive device according to an embodiment; An exploded view showing the configuration of the first assembly. FIG. 13 illustrates an assembly operation of the first assembly to the second assembly.

The vehicle drive device 100 according to the embodiment will be described below with reference to the drawings. As shown in FIG. 1, the vehicle drive device 100 is a device for driving a vehicle (hybrid vehicle) equipped with both an internal combustion engine EG and a rotating electric machine MG. Specifically, the vehicle drive device 100 is configured as a drive device for a one-motor parallel hybrid vehicle.

In the following description, unless otherwise specified, the "axial direction L,""radial direction R," and "circumferential direction" are defined based on the rotation axis of the rotating electric machine MG. In the radial direction R, the side of the rotation axis of the rotating electric machine MG is referred to as the "radial inner side R1," and the opposite side is referred to as the "radial outer side R2."
The directions of the components represent the directions when the components are assembled in the vehicle drive device 100. The terms related to the directions, positions, and the like of the components are concepts that include differences due to tolerances that may be tolerated in manufacturing.

As shown in FIG. 1, the vehicle drive device 100 includes an input member I, a rotating electric machine MG, a power transmission mechanism T, and a first engagement device CL1. In this embodiment, the vehicle drive device 100 further includes a second engagement device CL2, a counter gear mechanism CG, a differential gear mechanism DF, and a pair of output members O. In this embodiment, a portion of the input member I, a portion of the output member O, the first engagement device CL1, the second engagement device CL2, the rotating electric machine MG, the power transmission mechanism T, the counter gear mechanism CG, and the differential gear mechanism DF are housed within the case 1.

The rotating electric machine MG functions as a driving force source for the wheels W. The rotating electric machine MG can function as a motor (electric motor) that receives a supply of electric power to generate power, and as a generator (electric generator) that receives a supply of power to generate electric power. For this reason, the rotating electric machine MG is electrically connected to an electric storage device (battery, capacitor, etc.). The rotating electric machine MG receives a supply of electric power from the electric storage device to run as a power source, or supplies electric power generated by the torque of the internal combustion engine EG or the inertial force of the vehicle to the electric storage device for storage.

The internal combustion engine EG, like the rotating electric machine MG, functions as a driving force source for the wheels W. The internal combustion engine EG is a prime mover (gasoline engine, diesel engine, etc.) that is driven by the combustion of fuel to extract power.

The input member I is drivingly connected to the internal combustion engine EG. In this embodiment, the input member I is drivingly connected to the output shaft (crankshaft, etc.) of the internal combustion engine EG via a damper device (not shown) that attenuates fluctuations in the transmitted torque.

In this application, "driving connection" refers to a state in which two rotating elements are connected so as to be able to transmit a driving force, and includes a state in which the two rotating elements are connected so as to rotate integrally, or a state in which the two rotating elements are connected so as to be able to transmit a driving force via one or more transmission members. Such transmission members include various members that transmit rotation at the same speed or at a variable speed, such as shafts, gear mechanisms, belts, chains, etc. In addition, the transmission members may also include engagement devices that selectively transmit rotation and driving force, such as friction engagement devices and meshing engagement devices.

The first engagement device CL1 and the second engagement device CL2 are each an engagement device that connects and disconnects the power transmission between two rotating elements. As shown in FIG. 2, in this embodiment, the first engagement device CL1 and the second engagement device CL2 are arranged side by side in the axial direction L. Also, in this embodiment, the rotating electric machine MG and the power transmission mechanism T are arranged side by side in the axial direction L. And, the second engagement device CL2 is arranged on the side of the power transmission mechanism T in the axial direction L relative to the first engagement device CL1.

In the following description, in the axial direction L, the side on which the first engagement device CL1 is arranged relative to the second engagement device CL2 is referred to as the "axial first side L1," and the opposite side is referred to as the "axial second side L2."

As shown in FIG. 1, in this embodiment, the first engagement device CL1 is disposed in the power transmission path between the input member I and the rotating electric machine MG. Therefore, the first engagement device CL1 connects or disconnects the input member I and the rotating electric machine MG. In this embodiment, the engagement state (direct engagement state/slip engagement state/release state) of the first engagement device CL1 is controlled based on the hydraulic pressure supplied to the first engagement device CL1.

In this embodiment, the second engagement device CL2 is disposed in the power transmission path between the rotating electric machine MG and the power transmission mechanism T. The second engagement device CL2 connects or disconnects the power transmission mechanism T and the rotating electric machine MG. In this embodiment, the engagement state (direct engagement state/slip engagement state/disengagement state) of the second engagement device CL2 is controlled based on the hydraulic pressure supplied to the second engagement device CL2.

The power transmission mechanism T is configured to transmit the rotation transmitted from the rotating electric machine MG to the wheels W. In this embodiment, the power transmission mechanism T is a transmission TM.

The transmission TM is a device that has multiple gears with different gear ratios and changes the rotation transmitted from the rotating electric machine MG at a gear ratio corresponding to the formed gear. In this embodiment, the transmission TM changes the rotation and torque input to the transmission input shaft M, which is the input element of the transmission TM, according to the gear ratio at each time point, converts the torque, and transmits it to the transmission output gear G1, which is the output element of the transmission TM. In this embodiment, the transmission TM is an automatic stepped transmission that has multiple shift engagement devices and is switchable between multiple gears with different gear ratios. Note that the transmission TM may be an automatic continuously variable transmission that can change the gear ratio steplessly, or a manual stepped transmission that is switchable between multiple gears with different gear ratios.

The counter gear mechanism CG includes a counter input gear G2 and a counter output gear G3. The counter input gear G2 is an input element of the counter gear mechanism CG. The counter input gear G2 meshes with the transmission output gear G1. The counter output gear G3 is an output element of the counter gear mechanism CG. The counter output gear G3 is connected to the counter input gear G2 so as to rotate integrally with the counter input gear G2. In this embodiment, the counter output gear G3 is connected to the counter input gear G2 via a counter shaft S extending along the axial direction L. In the illustrated example, the counter output gear G3 is disposed on the first axial side L1 of the counter input gear G2.

The differential gear mechanism DF has a differential input gear G4 that meshes with the counter output gear G3 of the counter gear mechanism CG. The differential gear mechanism DF distributes the rotation of the differential input gear G4 to a pair of output members O that are each drivingly connected to the wheels W.

The vehicle drive device 100 configured as described above can transmit the torque of one or both of the internal combustion engine EG and the rotating electric machine MG to the wheels W by switching the engagement state of the first engagement device CL1 and the second engagement device CL2, thereby allowing the vehicle to run. Note that the vehicle drive device 100 according to this embodiment has a double-shaft configuration in which the input member I and the transmission input shaft M are arranged coaxially, and a pair of output members O are arranged parallel to each other on an axis different from that of the input member I and the transmission input shaft M. This configuration is suitable for the vehicle drive device 100 to be mounted on, for example, a front engine front drive (FF) vehicle.

In addition, in the vehicle drive device 100, when the internal combustion engine EG is started by the driving force of the rotating electric machine MG with the first engagement device CL1 in a direct engagement state and the second engagement device CL2 in a slipping engagement state, it is possible to prevent torque fluctuations at the start of the internal combustion engine EG from being transmitted to the wheels W. Here, the "direct engagement state" is an engagement state in which there is no rotational speed difference (slip) between a pair of friction plates of the friction engagement device. Also, the "slipping engagement state" is an engagement state in which there is a rotational speed difference (slip) between a pair of friction plates of the friction engagement device.

As shown in FIG. 2, in this embodiment, the case 1 includes a first side wall portion 11, a second side wall portion 12, and a cylindrical protrusion portion 13. Although not shown, the case 1 according to this embodiment includes a peripheral wall portion between the first side wall portion 11 and the second side wall portion 12 in the axial direction L that covers the rotating electric machine MG from the radial outside R2.

The first side wall portion 11 extends along the radial direction R. The first side wall portion 11 is disposed on the first axial side L1 relative to the rotating electric machine MG and the first engagement device CL1. The input member I penetrates the first side wall portion 11 in the axial direction L. The portion of the input member I closer to the first axial side L1 than the first side wall portion 11 is connected to the damper device described above.

The second side wall portion 12 extends along the radial direction R. The second side wall portion 12 is disposed on the second axial side L2 relative to the rotating electric machine MG and the second engagement device CL2. The transmission input shaft M penetrates the second side wall portion 12 in the axial direction L.

The cylindrical protrusion 13 is formed in a cylindrical shape that protrudes from the second side wall portion 12 in the axial direction L. In this embodiment, the cylindrical protrusion 13 is formed so as to protrude from the second side wall portion 12 to the first axial side L1. The cylindrical protrusion 13 is formed in a cylindrical shape that covers the radial outside R2 of the transmission input shaft M. In this embodiment, the end of the cylindrical protrusion 13 on the first axial side L1 is located closer to the second axial side L2 than the end of the input member I on the second axial side L2. In other words, the cylindrical protrusion 13 is spaced apart from the input member I in the axial direction L.

As shown in Figures 3 and 4, in this embodiment, the cylindrical protrusion 13 has an inner protrusion 131 and an outer protrusion 132. The inner protrusion 131 and the outer protrusion 132 are connected to each other with the outer peripheral surface of the inner protrusion 131 and the inner peripheral surface of the outer protrusion 132 in contact with each other. The end of the outer protrusion 132 on the first axial side L1 is located closer to the first axial side L1 than the end of the inner protrusion 131 on the first axial side L1.

In this embodiment, the input member I has an input tubular portion Ia that is formed into a cylindrical shape with an open end face on one side in the axial direction L (here, the second axial side L2). The transmission input shaft M has an insertion portion Ma that is inserted into the radial inner side R1 of the input tubular portion Ia. The input member I and the transmission input shaft M are configured to rotate relative to one another.

As shown in FIG. 2, the rotating electric machine MG includes a stator St and a rotor Ro arranged radially inward R1 with respect to the stator St. The stator St is fixed to a non-rotating member. In this embodiment, the stator St is fixed to the first side wall portion 11 of the case 1 by a fixing member such as a bolt. In this embodiment, the stator St includes a stator core Stc and a coil C wound around the stator core Stc so that a coil end portion Ce protruding from the stator core Stc to both sides in the axial direction L (the axial first side L1 and the axial second side L2) is formed. The rotor Ro is configured to be rotatable relative to the stator St. In this embodiment, the rotor Ro includes a rotor core Roc, a pair of holding members H that hold the rotor core Roc from both sides in the axial direction L, and a permanent magnet PM arranged in the rotor core Roc. In this embodiment, each of the stator core Stc and the rotor core Roc is formed by stacking multiple annular plate-shaped magnetic bodies (e.g., electromagnetic steel plates, etc.) in the axial direction L.

The vehicle drive device 100 includes a rotor support member 2 that supports the rotor Ro. The rotor support member 2 includes a cylindrical portion 21 and a flange portion 22.

The cylindrical portion 21 is formed in a cylindrical shape extending along the axial direction L and supports the rotor Ro from the radially inner side R1. The cylindrical portion 21 is connected to the rotor Ro so as to rotate integrally with the rotor Ro. In this embodiment, the rotor Ro is attached to the outer peripheral surface of the cylindrical portion 21. The rotor Ro is attached to the outer peripheral surface of the cylindrical portion 21 by, for example, welding, crimping, etc.

The flange portion 22 is formed to extend along the radial direction R on the radial inner side R1 relative to the cylindrical portion 21. In this embodiment, the flange portion 22 is disposed adjacent to the second axial side L2 relative to the second engagement device CL2. Also, in this embodiment, the flange portion 22 is disposed on the first axial side L1 relative to the second side wall portion 12. Also, in this embodiment, the flange portion 22 is formed in the shape of an annular plate extending along the radial direction R and the circumferential direction.

The flange portion 22 is connected to the cylindrical portion 21 so as to rotate integrally with the cylindrical portion 21. In this embodiment, the flange portion 22 is an independent member from the cylindrical portion 21 and is joined to the cylindrical portion 21 by, for example, welding, crimping, or the like. In other words, the cylindrical portion 21 and the flange portion 22, which are separate members, are joined together. In the illustrated example, the flange portion 22 and the cylindrical portion 21 are joined by welding so that the end of the radial outer side R2 of the flange portion 22 and the end of the axial second side L2 of the cylindrical portion 21 are connected to each other.

The first engagement device CL1 is disposed on the radial inner side R1 of the cylindrical portion 21 and on the first axial side L1 of the flange portion 22. In this way, in the rotor support member 2, a space for disposing the first engagement device CL1 is secured on the radial inner side R1 of the cylindrical portion 21 and on the first axial side L1 of the flange portion 22. Therefore, the rotor support member 2 is formed in a bottomed cylindrical shape that opens toward the first axial side L1. Furthermore, in this embodiment, the second engagement device CL2 is disposed between the first engagement device CL1 and the flange portion 22 in the axial direction L. Here, as described above, the first engagement device CL1 and the second engagement device CL2 are disposed side by side in the axial direction L. Therefore, the second engagement device CL2 is disposed adjacent to the first engagement device CL1 on the second axial side L2.

In this embodiment, the first engagement device CL1 and the second engagement device CL2 are arranged on the radial inside R1 of the rotor Ro, at a position overlapping with the rotor Ro when viewed radially along the radial direction R. Here, "radially inside R1" refers to being on the inside in the radial direction R of the target element, regardless of the position in the axial direction L. The same applies to "radially outside R2." In addition, with regard to the arrangement of two elements, "overlapping when viewed in a specific direction" refers to the existence of at least a portion of an area where a virtual line parallel to the line of sight intersects with both of the two elements when the virtual line is moved in each direction perpendicular to the virtual line.

As shown in FIG. 3, the first engagement device CL1 includes a first inner friction material 411 and a first outer friction material 412 arranged side by side in the axial direction L, and a first piston portion 42 that presses the first inner friction material 411 and the first outer friction material 412 in the axial direction L. In this embodiment, the first engagement device CL1 further includes a first hydraulic oil chamber 43 to which hydraulic oil for the first piston portion 42 is supplied, and an oil chamber forming member 46 that extends radially outward R2 relative to the input member I and is connected to rotate integrally with the input member I.

The first inner friction material 411 and the first outer friction material 412 are both formed in an annular plate shape and are arranged with their rotational axes aligned with each other. Furthermore, multiple pieces of the first inner friction material 411 and the first outer friction material 412 are provided, and these are arranged alternately along the axial direction L. Either one of the first inner friction material 411 and the first outer friction material 412 can be a friction plate, and the other can be a separate plate. In the following description, the first inner friction material 411 and the first outer friction material 412 may be collectively referred to as the "first friction member 41".

The first outer friction material 412 corresponds to the "first friction plate". The first outer friction material 412 is supported by the first outer support member 48. The first outer support member 48 is a member that supports the first outer friction material 412 from the radial outside R2. The first outer support member 48 opens toward the axial first side L1. The first outer support member 48 is configured to rotate integrally with the cylindrical portion 21. In this embodiment, the first outer support member 48 is formed integrally with the cylindrical portion 21. In the illustrated example, a plurality of splines extending in the axial direction L over the entire area of the axial direction L are formed on the inner peripheral portion of the cylindrical portion 21 in a circumferentially dispersed manner. On the other hand, a similar spline is also formed on the outer peripheral portion of the first outer friction material 412. Then, by engaging these splines with each other, the first outer friction material 412 is supported from the radial outside R2 by the cylindrical portion 21. In this way, the first outer friction material 412 is supported so as to be slidable in the axial direction L while its relative rotation with respect to the cylindrical portion 21 is restricted.

The first inner friction material 411 corresponds to the "second friction plate." The first inner friction material 411 is supported by the first inner support member 44. The first inner support member 44 is a member that supports the first inner friction material 411 from the radial inner side R1. The first inner support member 44 includes a first cylindrical support portion 441 formed in a cylindrical shape extending along the axial direction L, and a first radial extension portion 442 formed to extend from the first cylindrical support portion 441 to the radial inner side R1.

The first cylindrical support portion 441 supports the first inner friction material 411 from the radially inner side R1. In the illustrated example, a plurality of splines extending in the axial direction L are formed on the outer periphery of the first cylindrical support portion 441, distributed circumferentially over the entire area of the axial direction L. On the other hand, a similar spline is formed on the inner periphery of the first inner friction material 411. Then, by engaging these splines with each other, the first inner friction material 411 is supported from the radially inner side R1 by the first cylindrical support portion 441. In this way, the first inner friction material 411 is supported slidably in the axial direction L in a state in which relative rotation with respect to the first cylindrical support portion 441 is restricted.

The first radial extension portion 442 corresponds to a "radial extension support portion." The first radial extension portion 442 is connected to the first cylindrical support portion 441 so as to rotate integrally with the first cylindrical support portion 441. In this embodiment, the first radial extension portion 442 is a member independent of the first cylindrical support portion 441, and is joined to the first cylindrical support portion 441 by, for example, welding, crimping, or the like. In the illustrated example, the first radial extension portion 442 and the first cylindrical support portion 441 are joined to each other by welding in a state in which the surface of the axial first side L1 of the first radial extension portion 442 and the surface of the axial second side L2 of the first cylindrical support portion 441 are in contact with each other. In addition, the first radial extension portion 442 is connected to the input member I so as to rotate integrally with the input member I. In this embodiment, the end of the radial inner side R1 of the first radial extension portion 442 is connected to the outer circumferential surface of the input member I. In the illustrated example, the end of the first radially extending portion 442 on the radially inner side R1 is joined by welding to a flange-shaped protrusion formed on the outer circumferential surface of the input member I. In this embodiment, the first radially extending portion 442 is formed in the shape of an annular plate extending along the radial direction R and the circumferential direction.

In this embodiment, the first engagement device CL1 has an abutment portion 442a that abuts against the first friction member 41 from the side opposite to the side of the first piston portion 42 in the axial direction L (here, the second axial side L2). In the illustrated example, the abutment portion 442a is formed integrally with the first radial extension portion 442. Specifically, the abutment portion 442a is formed by a portion of the first radial extension portion 442 that extends radially outward R2 beyond the first cylindrical support portion 441. In this embodiment, the abutment portion 442a is disposed so as to abut against the first inner friction material 411 closest to the second axial side L2 from the second axial side L2.

The first radial extension portion 442 contacts the oil passage forming member 45 in the axial direction L. In this embodiment, the first radial extension portion 442 abuts against the oil passage forming member 45 from the second axial side L2.

The oil passage forming member 45 is a member that forms an oil passage in the first engagement device CL1. In this embodiment, the oil passage forming member 45 is disposed between the first radially extending portion 442 and the first piston portion 42 in the axial direction L. Furthermore, in this embodiment, the oil passage forming member 45 is disposed on the radial inner side R1 of the first cylindrical support portion 441, at a position that overlaps with the first cylindrical support portion 441 when viewed radially along the radial direction R. In this embodiment, the oil passage forming member 45 has a connecting portion 451 and a partition portion 452.

The connecting portion 451 is formed in a cylindrical shape extending along the axial direction L. The connecting portion 451 is connected to the first cylindrical support portion 441 of the first inner support member 44 so as to rotate integrally with the first cylindrical support portion 441. In this embodiment, the connecting portion 451 is connected to the first cylindrical support portion 441 in a state adjacent to the radial inner side R1 of the first cylindrical support portion 441. Specifically, a plurality of splines extending in the axial direction L are formed in a circumferentially distributed manner on the inner peripheral portion of the first cylindrical support portion 441. On the other hand, similar splines are formed on the outer peripheral portion of the connecting portion 451. Then, the connecting portion 451 is connected to the first cylindrical support portion 441 so as to rotate integrally with the first cylindrical support portion 441 by engaging these splines with each other.

The partition portion 452 is formed to extend from the connecting portion 451 to the radially inward side R1. In this embodiment, the partition portion 452 and the connecting portion 451 are integrally formed so that the end portion of the partition portion 452 on the radially outward side R2 and the end portion of the connecting portion 451 on the axial second side L2 are connected to each other. The partition portion 452 is disposed to separate the space between the first piston portion 42 and the first inner support member 44.

In this embodiment, a radial groove 45a is formed along the radial direction R on the contact surface of the oil passage forming member 45 with the first radial extension portion 442. In this embodiment, the partition portion 452 abuts against the first radial extension portion 442 from the axial first side L1 in at least a portion of the entire radial direction R of the partition portion 452. Then, a radial groove 45a is formed on the contact surface of the partition portion 452 with the first radial extension portion 442. The radial groove 45a is formed so as to be continuous over the entire radial direction R of the contact surface of the partition portion 452 with the first radial extension portion 442. In other words, the radial groove 45a is formed so as to communicate the radial inner side R1 and the radial outer side R2 with respect to the contact portion between the partition portion 452 and the first radial extension portion 442. In this embodiment, a plurality of radial grooves 45a are formed in a circumferentially distributed manner.

The first piston portion 42 is disposed on the first axial side L1 relative to the first radially extending portion 442 of the first inner support member 44. In this embodiment, the first piston portion 42 is supported so as to rotate integrally with the first inner support member 44. In this embodiment, although not shown, the connecting portion 451 restricts the relative rotation of the first piston portion 42 with respect to the connecting portion 451 so as to rotate integrally with the first piston portion 42. Here, as described above, the connecting portion 451 is connected to the first cylindrical support portion 441 of the first inner support member 44 so as to rotate integrally. Therefore, in this embodiment, the first piston portion 42 is supported so as to rotate integrally with the first inner support member 44 via the connecting portion 451.

In this embodiment, the first piston portion 42 is configured to press the first friction member 41 in the axial direction L with a pressure corresponding to the hydraulic pressure supplied to the first hydraulic oil chamber 43. The first piston portion 42 has a first sliding portion 421 and a first pressing portion 422.

The first sliding portion 421 extends along the radial direction R. In this embodiment, the first sliding portion 421 is formed in the shape of an annular plate extending along the radial direction R and the circumferential direction. The first sliding portion 421 is configured to slide in the axial direction L within the first cylinder portion C1. In this embodiment, the first sliding portion 421 is disposed radially inward R1 with respect to the first friction member 41, at a position overlapping with the first friction member 41 when viewed radially along the radial direction R.

The first cylinder portion C1 is formed in a cylindrical shape along the axial direction L. In this embodiment, the first cylinder portion C1 is formed by the input member I and the oil passage forming member 45. Specifically, a part of the outer peripheral surface of the input cylindrical portion Ia of the input member I functions as a sliding surface against which the end of the radially inner side R1 of the first sliding portion 421 slides. In addition, a part of the inner peripheral surface of the connecting portion 451 of the oil passage forming member 45 functions as a sliding surface against which the end of the radially outer side R2 of the first sliding portion 421 slides.

The first pressing portion 422 extends from the first sliding portion 421 to the radially outer side R2 so as to be adjacent to the first friction member 41 in the axial direction L. In this embodiment, the first pressing portion 422 is disposed on the opposite side (here, the axial first side L1) to the side of the abutting portion 442a of the first radially extending portion 442 in the axial direction L with respect to the first friction member 41. Therefore, the first pressing portion 422 is formed to extend from the end of the radially outer side R2 of the first sliding portion 421 to the radially outer side R2 while making a detour through the axial first side L1 with respect to the first cylindrical support portion 441.

In this embodiment, the first piston portion 42 is biased toward the first axial side L1 by the first biasing member 42a. The first biasing member 42a is disposed between the first sliding portion 421 and the partition portion 452 of the oil passage forming member 45 in the axial direction L. In this embodiment, a plurality of first biasing members 42a are disposed in a circumferentially dispersed manner. For example, a return spring or the like can be used as the first biasing member 42a. Thus, when oil of a predetermined hydraulic pressure is supplied from a hydraulic control device (not shown) to the first hydraulic oil chamber 43, the first piston portion 42 slides toward the second axial side L2 against the biasing force of the first biasing member 42a in response to the hydraulic pressure, and presses the first friction member 41 toward the second axial side L2.

The first hydraulic oil chamber 43 is disposed adjacent to the first piston portion 42 in the axial direction L. In this embodiment, the first hydraulic oil chamber 43 is formed between the first piston portion 42 and the oil chamber forming member 46. Specifically, the first hydraulic oil chamber 43 is formed between the first sliding portion 421 of the first piston portion 42 and the oil chamber forming member 46 in the axial direction L.

In this embodiment, the first hydraulic oil chamber 43 is arranged so as to overlap with the first friction member 41 when viewed in the radial direction along the radial direction R. Also, in this embodiment, the first hydraulic oil chamber 43 is arranged so as not to overlap with the first friction member 41 when viewed in the axial direction along the axial direction L.

In this embodiment, the oil chamber forming member 46 is arranged so as to contact the outer peripheral surface of the input cylindrical portion Ia of the input member I. Also, in this embodiment, the oil chamber forming member 46 is arranged on the first axial side L1 relative to the first piston portion 42. Here, the oil chamber forming member 46 is arranged adjacent to the first axial side L1 relative to the first sliding portion 421 of the first piston portion 42.

In this embodiment, the radial dimension R of the outermost portion of the oil chamber forming member 46 is smaller than the radial dimension R of the inner peripheral surface of the first cylindrical support portion 441. Also, in this embodiment, the oil chamber forming member 46 is disposed radially inward R1 than the connecting portion 451 of the oil passage forming member 45. Therefore, the first piston portion 42 is formed to extend to the axial first side L1 through between the oil chamber forming member 46 and the connecting portion 451 in the radial direction R, and further to the radially outward R2, so that the first pressing portion 422 is disposed radially outward R2 than the connecting portion 451.

In this embodiment, a first cancel oil chamber 47 is formed on the side of the first piston portion 42 opposite the side of the first hydraulic oil chamber 43 in the axial direction L (here, the second axial side L2). The first cancel oil chamber 47 is a space for generating hydraulic pressure that counteracts the centrifugal hydraulic pressure generated in the first hydraulic oil chamber 43. In this embodiment, the first cancel oil chamber 47 is formed between the first piston portion 42 and the oil passage forming member 45. In other words, the portion of the space between the first piston portion 42 and the first inner support member 44 on the first axial side L1 relative to the partition portion 452 of the oil passage forming member 45 functions as the first cancel oil chamber 47.

As shown in FIG. 3, the second engagement device CL2 includes a second inner friction material 511 and a second outer friction material 512 arranged side by side in the axial direction L, and a second piston portion 52 that presses the second inner friction material 511 and the second outer friction material 512 in the axial direction L. In this embodiment, the second engagement device CL2 further includes a second hydraulic oil chamber 53 to which hydraulic oil for the second piston portion 52 is supplied.

The second inner friction material 511 and the second outer friction material 512 are both formed in an annular plate shape and are arranged with their rotational axes aligned with each other. Furthermore, the second inner friction material 511 and the second outer friction material 512 are provided in multiple sheets, which are arranged alternately along the axial direction L. Either the second inner friction material 511 or the second outer friction material 512 can be a friction plate, and the other can be a separate plate. In the following description, the second inner friction material 511 and the second outer friction material 512 may be collectively referred to as the "second friction member 51".

The second inner friction material 511 corresponds to the "fourth friction plate." The second inner friction material 511 is supported by the second inner support member 54. The second inner support member 54 is a member that supports the second inner friction material 511 from the radial inner side R1. In this embodiment, the second inner support member 54 includes a second cylindrical support portion 541 formed in a cylindrical shape extending along the axial direction L, and a second radial extension portion 542 formed to extend from the second cylindrical support portion 541 to the radial inner side R1.

The second cylindrical support portion 541 supports the second inner friction material 511 from the radially inner side R1. In the illustrated example, a plurality of splines extending in the axial direction L are formed on the outer periphery of the second cylindrical support portion 541, distributed circumferentially over the entire area of the axial direction L. On the other hand, a similar spline is formed on the inner periphery of the second inner friction material 511. Then, by engaging these splines with each other, the second inner friction material 511 is supported from the radially inner side R1 by the second cylindrical support portion 541. In this way, the second inner friction material 511 is supported slidably in the axial direction L in a state in which relative rotation with respect to the second cylindrical support portion 541 is restricted.

The second radial extension portion 542 is connected to the second cylindrical support portion 541 so as to rotate integrally with the second cylindrical support portion 541. In this embodiment, the second radial extension portion 542 is a member independent of the second cylindrical support portion 541 and is joined to the second cylindrical support portion 541 by, for example, welding, crimping, or the like. In the illustrated example, the second radial extension portion 542 and the second cylindrical support portion 541 are joined by welding so that the end of the second radial extension portion 542 on the radial outer side R2 and the end of the second cylindrical support portion 541 on the axial first side L1 are connected to each other. In this embodiment, the second radial extension portion 542 is formed in the shape of an annular plate extending along the radial direction R and the circumferential direction.

The second radial extension portion 542 is connected to the transmission input shaft M so as to rotate integrally with the transmission input shaft M. In this embodiment, the end of the second radial extension portion 542 on the radially inner side R1 is connected to the outer circumferential surface of the transmission input shaft M. In the illustrated example, a plurality of splines extending in the axial direction L are formed and distributed in the circumferential direction on the inner circumferential surface of the cylindrical portion formed at the end of the second radial extension portion 542 on the radially inner side R1. On the other hand, similar splines are formed on the outer circumferential surface of the transmission input shaft M. Then, the second radial extension portion 542 and the transmission input shaft M are connected to rotate integrally with each other by engaging with each other with the splines.

The second outer friction material 512 corresponds to the "third friction plate". The second outer friction material 512 is supported by the second outer support member 55. The second outer support member 55 is a member that supports the second outer friction material 512 from the radial outside R2. In this embodiment, the second outer support member 55 is formed in a cylindrical shape extending along the axial direction L. In the illustrated example, a plurality of splines extending in the axial direction L are formed in the inner peripheral portion of the second outer support member 55 and distributed in the circumferential direction. On the other hand, a similar spline is formed on the outer peripheral portion of the second outer friction material 512. Then, by engaging these splines with each other, the second outer friction material 512 is supported from the radial outside R2 by the second outer support member 55. In this way, the second outer friction material 512 is supported slidably in the axial direction L in a state in which the relative rotation with respect to the second outer support member 55 is restricted.

The second outer support member 55 is configured to rotate integrally with the rotor support member 2. In this embodiment, the second outer support member 55 is supported from the radial outside R2 by the cylindrical portion 21 of the rotor support member 2. In the illustrated example, a plurality of splines extending in the axial direction L are formed in a circumferentially distributed manner on the outer periphery of the second outer support member 55. On the other hand, as described above, a plurality of splines extending in the axial direction L are also formed in a circumferentially distributed manner on the inner periphery of the cylindrical portion 21. Then, by engaging these splines with each other, the second outer support member 55 is supported from the radial outside R2 by the cylindrical portion 21. In this way, the second outer friction material 512 is supported by the cylindrical portion 21 of the rotor support member 2 via the second outer support member 55.

In the present embodiment, the second engagement device CL2 includes a contact member 56 that contacts the second friction member 51. The contact member 56 is disposed so as to contact the second friction member 51 from the side opposite to the side of the second piston portion 52 in the axial direction L (here, the first axial side L1). In the present embodiment, the contact member 56 is disposed so as to contact the second outer friction material 512 that is closest to the first axial side L1, from the first axial side L1.
In this embodiment, the abutment member 56 is supported from the radial outside R2 by the cylindrical portion 21. In the illustrated example, a plurality of splines extending in the axial direction L are formed on the outer periphery of the abutment member 56 in a circumferentially distributed manner. These splines are engaged with a plurality of splines formed on the inner periphery of the cylindrical portion 21, so that the abutment member 56 is supported from the radial outside R2 by the cylindrical portion 21 in a state in which the relative rotation of the abutment member 56 with respect to the cylindrical portion 21 is restricted and the abutment member 56 is slidable in the axial direction L. In the illustrated example, a circular fixing member 56a is fixed to the inner periphery of the cylindrical portion 21 so as to abut against the abutment member 56 from the first axial side L1. In this way, the movement of the abutment member 56 to the first axial side L1 is restricted by the fixing member 56a. In this embodiment, the fixing member 56a is a snap ring.

In this embodiment, the second piston portion 52 is configured to press the second friction member 51 in the axial direction L with a pressure corresponding to the hydraulic pressure supplied to the second hydraulic oil chamber 53. Also, in this embodiment, the second piston portion 52 is disposed on the second axial side L2 from the second friction member 51. In other words, the second piston portion 52 is disposed so as not to overlap with the second friction member 51 when viewed in the radial direction along the radial direction R. The second piston portion 52 has a second sliding portion 521 and a second pressing portion 522.

The second sliding portion 521 is configured to slide in the axial direction L inside the second cylinder portion C2. The second cylinder portion C2 is formed in a cylindrical shape along the axial direction L. In this embodiment, the second cylinder portion C2 is formed by the cylinder forming portion 23 of the flange portion 22. In other words, in this embodiment, a part of the flange portion 22 constitutes a part of the second engagement device CL2.

The cylinder forming portion 23 protrudes to the second axial side L2 to form the second cylinder portion C2 along which the second piston portion 52 slides. In this embodiment, the cylinder forming portion 23 has an inner cylindrical portion 231, an outer cylindrical portion 232, and a radial connecting portion 233.

The inner cylindrical portion 231 is formed in a cylindrical shape extending along the axial direction L. A part of the outer peripheral surface of the inner cylindrical portion 231 functions as a sliding surface against which the end of the radially inner side R1 of the second sliding portion 521 slides. In this embodiment, the inner cylindrical portion 231 is disposed so as to cover the radially outer side R2 of the cylindrical protruding portion 13 of the case 1.

The outer cylindrical portion 232 is formed in a cylindrical shape extending along the axial direction L. The outer cylindrical portion 232 is disposed radially outward R2 relative to the inner cylindrical portion 231. A portion of the inner peripheral surface of the outer cylindrical portion 232 functions as a sliding surface against which the end of the second sliding portion 521 on the radially outward R2 slides.

The radial connecting portion 233 extends along the radial direction R so as to connect the inner cylindrical portion 231 and the outer cylindrical portion 232. In this embodiment, the radial connecting portion 233 is formed in the shape of an annular plate extending along the radial direction R and the circumferential direction. In this embodiment, the radial inner end R1 of the radial connecting portion 233 is connected to the end of the axial second side L2 of the inner cylindrical portion 231. The radial outer end R2 of the radial connecting portion 233 is connected to the end of the axial second side L2 of the outer cylindrical portion 232. In addition, the part of the flange portion 22 that is radially outer R2 than the cylinder forming portion 23 is formed in the shape of an annular plate extending along the radial direction R and the circumferential direction, and is connected to the end of the axial first side L1 of the outer cylindrical portion 232. In the illustrated example, the flange portion 22, which includes the inner cylindrical portion 231, the outer cylindrical portion 232, and the radial connecting portion 233, is integrally formed from a single member.

The second pressing portion 522 extends radially outward R2 from the second sliding portion 521. In this embodiment, the second pressing portion 522 is disposed on the opposite side of the second friction member 51 from the side of the abutting member 56 in the axial direction L (here, the second axial side L2).

The second piston portion 52 is supported so as to rotate integrally with the rotor support member 2. In this embodiment, although not shown, the flange portion 22 of the rotor support member 2 restricts the relative rotation of the second piston portion 52 with respect to the flange portion 22 so that the flange portion 22 rotates integrally with the second piston portion 52.

In this embodiment, the second piston portion 52 is biased toward the second axial side L2 by the second biasing member 52a attached to the mounting member 57. The second biasing member 52a is disposed between the second sliding portion 521 and the mounting member 57 in the axial direction L. In this embodiment, a plurality of second biasing members 52a are disposed in a circumferentially dispersed manner. For example, a return spring or the like can be used as the second biasing member 52a. Thus, when oil of a predetermined hydraulic pressure is supplied from a hydraulic control device (not shown) to the second hydraulic oil chamber 53, the second piston portion 52 slides toward the first axial side L1 against the biasing force of the second biasing member 52a in response to the hydraulic pressure, and presses the second friction member 51 toward the first axial side L1.

The mounting member 57 is disposed radially outwardly R2 relative to the inner cylindrical portion 231 of the cylinder forming portion 23. In this embodiment, the mounting member 57 is disposed so as to contact the outer peripheral surface of the inner cylindrical portion 231. Also, in this embodiment, the mounting member 57 is disposed adjacent to the first axial side L1 relative to the second sliding portion 521 of the second piston portion 52.

The second hydraulic oil chamber 53 is disposed adjacent to the second piston portion 52 in the axial direction L. In this embodiment, the second hydraulic oil chamber 53 is formed between the second piston portion 52 and the cylinder forming portion 23. Specifically, the second hydraulic oil chamber 53 is formed between the second sliding portion 521 of the second piston portion 52 and the radial connecting portion 233 of the cylinder forming portion 23 in the axial direction L.

In this embodiment, the second hydraulic oil chamber 53 is arranged so as to overlap with the second friction member 51 when viewed in the axial direction along the axial direction L. Also, in this embodiment, the second hydraulic oil chamber 53 is arranged so as not to overlap with the second friction member 51 when viewed in the radial direction along the radial direction R.

In this embodiment, a second cancel oil chamber 58 is formed on the side of the second piston portion 52 opposite the side of the second hydraulic oil chamber 53 in the axial direction L (here, the first axial side L1). The second cancel oil chamber 58 is a space for generating hydraulic pressure that counteracts the centrifugal hydraulic pressure generated in the second hydraulic oil chamber 53. In this embodiment, the second cancel oil chamber 58 is formed between the second piston portion 52 and the mounting member 57.

In this embodiment, the flange portion 22 extends radially inward R1 from the second engagement device CL2. In the illustrated example, the inner peripheral end of the flange portion 22 is located radially inward R1 from the inner peripheral end of the second piston portion 52.

As shown in FIG. 3, the vehicle drive device 100 includes an annular member 10 fixed to the inner periphery of the cylindrical portion 21. The annular member 10 is formed in an annular shape extending in the circumferential direction. In this embodiment, the annular member 10 is a snap ring. The annular member 10 is fixed to the cylindrical portion 21 by being fitted into a second fixing groove 21d (see FIG. 5) formed in the inner periphery of the cylindrical portion 21. The second fixing groove 21d is a groove formed continuously in the circumferential direction on the inner periphery of the cylindrical portion 21. In this example, as described above, a plurality of splines extending in the axial direction L are formed in the inner periphery of the cylindrical portion 21 in a distributed manner in the circumferential direction. The second fixing groove 21d is formed at least in the protruding portion protruding radially inward R1 of such a plurality of splines.

The annular member 10 is disposed on the first axial side L1 relative to the first inner friction material 411 and the first outer friction material 412, and is disposed at a position overlapping at least one of the first piston portion 42 and the first inner friction material 411 in the axial view along the axial direction L. In the illustrated example, the outer peripheral edge of the first piston portion 42 and the outer peripheral edge of the first inner friction material 411 are disposed at approximately the same position in the radial direction R. Therefore, the annular member 10 is configured to overlap both the first pressing portion 422 of the first piston portion 42 and the first inner friction material 411. Note that, when the positions of the outer peripheral edge of the first piston portion 42 and the outer peripheral edge of the first inner friction material 411 in the radial direction R are different, the annular member 10 is disposed so as to overlap at least one of the first piston portion 42 and the first inner friction material 411 that is disposed on the radial outer side R2 in the axial view.

As shown in FIG. 2, in this embodiment, the following formula (1) holds.
D1-D2 <D3 ...(1)

In the above formula (1), D1 is the diameter of the inner peripheral surface of the cylindrical portion 21. And D2 is the outermost diameter of the first piston portion 42. Also, D3 is the distance in the radial direction R from the inner peripheral surface of the cylindrical portion 21 to the inner peripheral end of the annular member 10. Here, the inner peripheral surface of the cylindrical portion 21 is a cylindrical surface facing the radially inner side R1 of the cylindrical portion 21. In the illustrated example, the inner peripheral surface of the cylindrical portion 21 refers to a virtual surface formed by connecting the ends of the radially inner side R1 of the multiple splines formed on the inner peripheral portion of the cylindrical portion 21. Also, in this embodiment, the outermost diameter of the first piston portion 42 is the diameter of the outer edge of the first pressing portion 422.

As shown in FIG. 3, in this embodiment, the vehicle drive device 100 includes a rotation sensor 3 that detects the rotation of the rotor Ro. The rotation sensor 3 is a sensor for detecting at least one of the position of the rotor Ro in the rotational direction relative to the stator St and the rotation speed of the rotor Ro. For example, a resolver can be used as such a rotation sensor 3. The rotation sensor 3 includes a rotating body 31 and a fixed body 32. In this embodiment, each of the rotating body 31 and the fixed body 32 is formed in a circular ring shape based on the rotation axis of the rotor Ro.

The rotating body 31 is supported on the outer peripheral surface of the cylinder forming portion 23. That is, the rotating body 31 is disposed on the radial outer side R2 of the cylinder forming portion 23, and is disposed at a position overlapping with the cylinder forming portion 23 when viewed in the radial direction along the radial direction R. In this embodiment, the rotating body 31 is disposed on the outer peripheral surface of the outer cylindrical portion 232 in the cylinder forming portion 23. The rotating body 31 is connected to the outer cylindrical portion 232 so as to rotate integrally with the outer cylindrical portion 232. In the illustrated example, a plurality of splines extending in the axial direction L are formed on the outer peripheral surface of the cylinder forming portion 23 (here, the outer cylindrical portion 232) in a circumferentially distributed manner. On the other hand, a similar spline is also formed on the inner peripheral surface of the rotating body 31. The splines engage with each other, and the rotating body 31 and the rotor support member 2 are connected to rotate integrally with each other. In the illustrated example, an annular restricting member 31a is fixed to the outer peripheral surface of the outer cylindrical portion 232 so as to abut against the rotating body 31 from the second axial side L2. In this way, movement of the rotor 31 toward the second axial side L2 is restricted by the restricting member 31a.

The fixed body 32 is disposed radially outwardly R2 from the rotating body 31. The fixed body 32 is supported by a non-rotating member. In this embodiment, the fixed body 32 is supported by a sensor support portion 14 provided on the second side wall portion 12 of the case 1.

In this embodiment, the rotation sensor 3 is disposed on the radial outer side R2 of the second sliding portion 521 of the second piston portion 52, and is disposed at a position overlapping the second sliding portion 521 in a radial view along the radial direction R. Also, in this embodiment, the rotation sensor 3 is disposed so as to overlap the second friction member 51 in an axial view along the axial direction L. In the illustrated example, the rotating body 31 is disposed so as to overlap the second pressing portion 522 of the second piston portion 52 in addition to the second friction member 51 in an axial view. Furthermore, in this embodiment, the rotation sensor 3 is disposed so as to overlap the rotor Ro in an axial view along the axial direction L. In the illustrated example, the radial outer side R2 portion of the fixed body 32 is disposed so as to overlap the rotor Ro in an axial view.

As shown in FIG. 3, in this embodiment, the vehicle drive device 100 includes a first bearing B1 and a second bearing B2 that rotatably support the rotor support member 2, and a third bearing B3 that rotatably supports the input member I. In this embodiment, each of the first bearing B1, the second bearing B2, and the third bearing B3 is a ball bearing.

The first bearing B1 rotatably supports the cylindrical portion 21 of the rotor support member 2. In this embodiment, the first bearing B1 is disposed radially outward R2 from the first cylindrical support portion 441 of the first inner support member 44. In this embodiment, the first bearing B1 is disposed on the first axial side L1 with respect to the rotor Ro. In this embodiment, the first bearing B1 is disposed on the outer peripheral surface of the cylindrical portion 21. Specifically, the cylindrical portion 21 has a bearing support portion 211 that protrudes toward the first axial side L1 from the rotor Ro. The first bearing B1 is attached so that the inner peripheral surface of the first bearing B1 is in contact with the outer peripheral surface of the bearing support portion 211. In this embodiment, the first bearing B1 is supported by the bearing support portion 11a of the first side wall portion 11 in the case 1. The bearing support portion 11a protrudes toward the second axial side L2 and supports the first bearing B1 from the radial outer side R2. In this way, the first bearing B1 rotatably supports the cylindrical portion 21 relative to the first side wall portion 11.

In this embodiment, the first bearing B1 is arranged so as to overlap with the first piston portion 42 when viewed in the radial direction R. Specifically, the first bearing B1 is arranged so as to overlap with the first pressing portion 422 of the first piston portion 42 when viewed in the radial direction. Also, in this embodiment, the first bearing B1 is arranged so as to overlap with the rotor Ro when viewed in the axial direction L. Also, in this embodiment, the first bearing B1 is arranged so as to overlap with the coil end portion Ce of the stator St when viewed in the radial direction R (see FIG. 2).

In this embodiment, the cylindrical portion 21 is formed with a protrusion 21a that protrudes from the outer peripheral surface of the cylindrical portion 21 to the radially outward side R2 on the first axial side L1 relative to the rotor Ro. Here, the protrusion 21a is formed continuously over the entire circumferential area. The protrusion 21a is arranged so as to be sandwiched between the rotor Ro and the first bearing B1 from both sides in the axial direction L. Specifically, the rotor Ro is arranged so as to abut against the protrusion 21a from the second axial side L2. The first bearing B1 is also arranged so as to abut against the protrusion 21a from the first axial side L1.

The second bearing B2 rotatably supports the flange portion 22 of the rotor support member 2. In this embodiment, the second bearing B2 is arranged so as to overlap with the second piston portion 52 when viewed in the radial direction R. In this embodiment, the second bearing B2 is arranged on the radial inner side R1 of the cylinder forming portion 23 of the flange portion 22, and is arranged at a position overlapping with the cylinder forming portion 23 when viewed in the radial direction R. The second bearing B2 supports the rotor support member 2 from the radial inner side R1. In the illustrated example, the second bearing B2 is interposed between the inner cylindrical portion 231 of the rotor support member 2 and the cylindrical protruding portion 13 (specifically, the outer protruding portion 132) of the case 1.

In this embodiment, the third bearing B3 is disposed on the radial inner side R1 relative to at least a portion of the first piston portion 42, and is disposed at a position overlapping with the first piston portion 42 as viewed in the radial direction along the radial direction R. Here, the third bearing B3 is disposed on the radial inner side R1 relative to the first pressing portion 422 of the first piston portion 42. Also, the third bearing B3 is disposed so as to overlap with the first pressing portion 422 as viewed in the radial direction. Furthermore, in this embodiment, the third bearing B3 is disposed on the first axial side L1 relative to the oil chamber forming member 46. Also, the third bearing B3 is disposed on the radial inner side R1 relative to a portion of the oil chamber forming member 46.

In this embodiment, the third bearing B3 is disposed on the outer peripheral surface of the input cylindrical portion Ia of the input member I. Specifically, the third bearing B3 is attached so that the inner peripheral surface of the third bearing B3 contacts the outer peripheral surface of the input cylindrical portion Ia. The third bearing B3 is also supported from the radial outside R2 by the first side wall portion 11 of the case 1. In this way, the third bearing B3 supports the input member I rotatably relative to the first side wall portion 11.

In this embodiment, the inner race of the third bearing B3 abuts against a step formed on the outer circumferential surface of the input cylindrical portion Ia from the first axial side L1. The outer race of the third bearing B3 abuts against the first side wall portion 11 from the second axial side L2. In this way, the movement of the third bearing B3 in the axial direction L is restricted by the input cylindrical portion Ia and the first side wall portion 11. As a result, the third bearing B3 is able to support a thrust load acting on the input member I supported by the third bearing B3.

As shown in FIG. 3, in this embodiment, the vehicle drive device 100 is provided with an oil passage for supplying oil to the first hydraulic oil chamber 43 to operate the first piston portion 42. This oil passage includes a first hydraulic oil passage P11, a first operating connection oil passage P12, and a second in-shaft oil passage P13.

The first hydraulic oil passage P11 is an oil passage that communicates with the first hydraulic oil chamber 43. The first hydraulic oil passage P11 is formed from the inner peripheral surface to the outer peripheral surface of the input cylindrical portion Ia of the input member I.

The first working oil passage P12 is an oil passage that connects the first working oil passage P11 and the second in-shaft oil passage P13. The first working oil passage P12 is formed in the insertion portion Ma of the transmission input shaft M. In this embodiment, the first working oil passage P12 is formed along the radial direction R from the second in-shaft oil passage P13 inside the insertion portion Ma to the outer circumferential surface.

The second in-shaft oil passage P13 is an oil passage formed inside the transmission input shaft M. In this embodiment, the second in-shaft oil passage P13 is formed along the axial direction L.

In addition, in this embodiment, the vehicle drive device 100 is provided with an oil passage for supplying oil to the second hydraulic oil chamber 53 to operate the second piston portion 52. This oil passage includes a second hydraulic oil passage P21, a second operating connection oil passage P22, and a second radial oil passage P23.

The second hydraulic oil passage P21 is an oil passage that connects the radial inner side R1 of the rotor support member 2 with the second hydraulic oil chamber 53. In this embodiment, the second hydraulic oil passage P21 is formed in the inner cylindrical portion 231 of the cylinder forming portion 23. The second hydraulic oil passage P21 is formed from the inner peripheral surface to the outer peripheral surface of the inner cylindrical portion 231.

The second working connection oil passage P22 is an oil passage that connects the second radial oil passage P23 and the second working oil passage P21. The second working connection oil passage P22 is formed in the cylindrical protrusion 13 of the case 1. In this embodiment, the second working connection oil passage P22 has an axial groove P22a formed to extend along the axial direction L at the abutment portion between the outer circumferential surface of the inner protrusion 131 and the inner circumferential surface of the outer protrusion 132, a circumferential groove P22b formed to extend along the circumferential direction on the outer circumferential surface of the outer protrusion 132, and a connection hole P22c formed along the radial direction R to connect the axial groove P22a and the circumferential groove P22b.

The second radial oil passage P23 is an oil passage formed in the second side wall portion 12 of the case 1. The second radial oil passage P23 is formed along the radial direction R.

As shown in FIG. 4, in this embodiment, the vehicle drive device 100 includes an oil passage for supplying oil to the first friction member 41 to lubricate the first friction member 41. This oil passage includes a first lubricating oil passage P31, a lubrication connection oil passage P32, and a first intra-shaft oil passage P33. The oil supplied to the first friction member 41 in this manner also serves to cool the first friction member 41.

The first lubricating oil passage P31 is an oil passage that supplies oil for lubricating the first friction member 41 to the first communication hole 44a of the first inner support member 44. The first lubricating oil passage P31 is formed from the inner peripheral surface to the outer peripheral surface of the input cylindrical portion Ia of the input member I. In this embodiment, the first lubricating oil passage P31 communicates with the space between the first piston portion 42 and the first inner support member 44. The first communication hole 44a corresponds to a "second supply hole" that penetrates the first inner support member 44 in the radial direction R. In this embodiment, the first communication hole 44a is formed to penetrate the first cylindrical support portion 441 of the first inner support member 44 in the radial direction R.

The lubrication connection oil passage P32 is an oil passage that connects the first lubrication oil passage P31 and the first in-shaft oil passage P33. The lubrication connection oil passage P32 is formed in the insertion portion Ma of the transmission input shaft M. In this embodiment, the lubrication connection oil passage P32 is formed along the radial direction R from the first in-shaft oil passage P33 inside the insertion portion Ma to the outer circumferential surface.

The first in-shaft oil passage P33 is an oil passage formed inside the transmission input shaft M. In this embodiment, the first in-shaft oil passage P33 is formed along the axial direction L. In this embodiment, the first in-shaft oil passage P33 is formed independently of the second in-shaft oil passage P13.

In this embodiment, the oil that flows through the first shaft oil passage P33, the lubrication connection oil passage P32, and the first lubricating oil passage P31 in order flows into the space between the first piston portion 42 and the first inner support member 44. Then, the oil that flows into this space branches into the space between the first inner support member 44 and the oil passage forming member 45 and the space between the first piston portion 42 and the oil passage forming member 45 (first cancel oil chamber 47) and flows toward the radially outer side R2. Here, the first cancel oil chamber 47, which is the space between the first piston portion 42 and the oil passage forming member 45, is a closed space except for the communication part with the first lubricating oil passage P31. Therefore, after the first cancel oil chamber 47 is filled with oil, the oil from the first lubricating oil passage P31 mainly flows into the space between the first inner support member 44 and the oil passage forming member 45. Then, the oil that flows into the space between the first inner support member 44 and the oil passage forming member 45 passes through the radial groove 45a and reaches the inner periphery of the first cylindrical support part 441. In this embodiment, the oil flow path to the inner periphery of the first cylindrical support part 441 functions as a supply part SP that supplies oil from the radial inside R1 to the inner periphery of the first inner support member 44.

The oil supplied to the inner circumference of the first cylindrical support portion 441 then passes through the first communication hole 44a and reaches the first friction member 41. In this way, the first friction member 41 is lubricated and cooled by the oil. The oil supplied to the first friction member 41 then passes through the gap between the first inner friction material 411 and the first outer friction material 412, and reaches the inner circumference of the cylindrical portion 21.

As shown in FIG. 3, in this embodiment, the oil supplied to the inner periphery of the cylindrical portion 21 passes through the rotor cooling hole 21b and is supplied to the oil passage for cooling the rotor Ro. The rotor cooling hole 21b corresponds to a "first supply hole" that communicates with the oil passage for cooling the rotor Ro. In this embodiment, the gap G between the outer periphery of the cylindrical portion 21 and the inner periphery of the rotor core Roc functions as an oil passage for cooling the rotor Ro. In this example, the oil supplied to this gap G flows in the axial direction L along the inner periphery of the rotor core Roc to cool the rotor Ro, and is then discharged from a discharge hole (not shown) and supplied to the coil end portion Ce of the stator St, etc.

In this embodiment, the rotor cooling holes 21b are formed so as to open to the inner peripheral portion of the cylindrical portion 21 on the second axial side L2 relative to the annular member 10. Also, in this embodiment, the rotor cooling holes 21b are formed so as to open to the outer peripheral portion of the cylindrical portion 21 on the second axial side L2 relative to the protrusion 21a. In the illustrated example, two rotor cooling holes 21b are formed side by side in the axial direction L.

As shown in FIG. 4, in this embodiment, the vehicle drive device 100 is provided with an oil passage for supplying oil to the second friction member 51 to lubricate the second friction member 51. This oil passage includes a second lubricating oil passage P41 and a first radial oil passage P42. The oil supplied to the second friction member 51 in this manner also serves to cool the second friction member 51.

The second lubricating oil passage P41 is an oil passage that supplies oil for lubricating the second friction member 51 to the second communication hole 54a of the second inner support member 54. The second communication hole 54a is formed to penetrate the second inner support member 54 in the radial direction R. In this embodiment, the second communication hole 54a is formed to penetrate the second cylindrical support portion 541 of the second inner support member 54 in the radial direction R.

The second lubricating oil passage P41 is formed in the cylindrical protrusion 13 of the case 1. In this embodiment, the second lubricating oil passage P41 has an axial groove P41a formed to extend along the axial direction L at the abutment between the outer peripheral surface of the inner protrusion 131 and the inner peripheral surface of the outer protrusion 132, a cylindrical oil passage P41b formed by being surrounded by the inner peripheral surface of the outer protrusion 132 on the axial first side L1 further than the end of the inner protrusion 131 on the axial first side L1, and a connection hole P41c formed along the radial direction R to connect the cylindrical oil passage P41b and the outer peripheral surface of the outer protrusion 132.

The first radial oil passage P42 is an oil passage formed in the second side wall portion 12 of the case 1. The first radial oil passage P42 is formed along the radial direction R. In this embodiment, the first radial oil passage P42 is formed independently of the second radial oil passage P23.

In this embodiment, the oil that flows sequentially through the first radial oil passage P42 and the second lubricating oil passage P41 flows into the space between the flange portion 22 and the second inner support member 54 from the connection hole P41c and the opening at the end of the cylindrical oil passage P41b on the first axial side L1.

The oil flowing in from the connection hole P41c passes through the first through hole 24a and the second through hole 231a in order to reach the second cancel oil chamber 58. The first through hole 24a is formed to penetrate the fitting member 24 in the radial direction R. The fitting member 24 is a member that is fitted to the inner circumferential surface of the inner cylindrical portion 231 of the cylinder forming portion 23 so as to abut against the second bearing B2 from the axial first side L1. The second through hole 231a is formed to penetrate the inner cylindrical portion 231 of the cylinder forming portion 23 in the radial direction R. The opening of the second through hole 231a on the radial outer side R2 opens into the second cancel oil chamber 58. Here, the second cancel oil chamber 58 is a closed space except for the portion communicating with the second through hole 231a. Therefore, after the second cancellation oil chamber 58 is filled with oil, the oil from the second lubricating oil passage P41 mainly flows out from the opening at the end of the cylindrical oil passage P41b on the first axial side L1.

In this way, the oil flowing out from the opening at the end of the cylindrical oil passage P41b on the first axial side L1 passes between the fitting member 24 and the second radially extending portion 542 of the second inner support member 54, and then passes through the second communication hole 54a to reach the second friction member 51.

Below, with reference to Figures 5 and 6, an example of the work of assembling a first assembly AS1 including the rotor Ro, rotor support member 2, and first engagement device CL1 to a second assembly AS2 that is separate from the first assembly AS1 is described. In this example, the work of assembling the first assembly AS1 including the rotor Ro, rotor support member 2, and first engagement device CL1 to a second assembly AS2 including the transmission TM is performed (see Figure 6). In this example, the first assembly AS1 is produced as follows.

First, as shown in FIG. 5, the rotor support member 2, the rotor Ro, the rotor 31 of the rotation sensor 3, the second piston portion 52, the mounting member 57, and the second outer support member 55 are assembled so that they rotate integrally. Furthermore, the second bearing B2 is assembled to the rotor support member 2. The second bearing B2 is inserted from the first axial side L1 into the radial inner side R1 of the inner cylindrical portion 231 so that the outer peripheral surface of the second bearing B2 contacts the inner peripheral surface of the inner cylindrical portion 231 of the cylinder forming portion 23. After that, the fitting member 24 is fitted to the inner peripheral surface of the inner cylindrical portion 231 so as to abut against the second bearing B2 from the first axial side L1.

Next, in a state where the second inner friction material 511 and the second outer friction material 512 are arranged alternately in the axial direction L, the second cylindrical support portion 541 of the second inner support member 54 is spline-engaged with the plurality of second inner friction materials 511. Then, the plurality of second outer friction materials 512 are spline-engaged with the second outer support member 55, and the abutting member 56 that is abutted from the axial first side L1 to the second outer friction material 512 closest to the axial first side L1 is spline-engaged with the cylindrical portion 21. After that, in a state where the abutting member 56 is positioned closer to the axial second side L2 than the first fixing groove 21c formed in the inner periphery of the cylindrical portion 21, the fixing member 56a is attached to the first fixing groove 21c. The first fixing groove 21c is a groove formed continuously in the circumferential direction on the inner periphery of the cylindrical portion 21.

Next, in a state where the first inner friction material 411 and the first outer friction material 412 are arranged alternately in the axial direction L, the first cylindrical support portion 441 of the first inner support member 44 and the multiple first inner friction materials 411 are spline-engaged. Here, the first inner support member 44 and the input member I are integrally connected. Furthermore, the oil passage forming member 45, the first piston portion 42, and the oil chamber forming member 46 are assembled to the input member I. As a result, the input member I, the first inner support member 44, the oil passage forming member 45, the first piston portion 42, and the oil chamber forming member 46 are connected so as to rotate integrally. Then, the multiple first outer friction materials 412 and the cylindrical portion 21 are spline-engaged. Then, the annular member 10 is attached to the second fixing groove 21d in a state where the first pressing portion 422 of the first piston portion 42 is located on the second axial side L2 from the second fixing groove 21d formed on the inner periphery of the cylindrical portion 21. The second fixing groove 21d is disposed on the first axial side L1 from the first fixing groove 21c.

As shown in FIG. 6, the assembly work of the first assembly AS1 to the second assembly AS2 is performed while maintaining the posture of the first assembly AS1 so that the rotation axis (axial direction L) of the rotor Ro is aligned vertically. In this example, the input member I of the first assembly AS1 is held by a holding device (not shown) so that the second engagement device CL2 is positioned lower than the first engagement device CL1. Meanwhile, the second assembly AS2 is positioned so that the insertion portion Ma of the transmission input shaft M faces upward. Then, the first assembly AS1 is brought close to the second assembly AS2 from above, and the insertion portion Ma of the transmission input shaft M is inserted into the radial inner side R1 of the input cylindrical portion Ia of the input member I.

At this time, due to the weight of the rotor Ro etc. supported by the cylindrical portion 21 of the rotor support member 2, the rotor support member 2 including the cylindrical portion 21 spline-engaged with the first outer friction material 412 moves downward relative to the input member I together with the second engagement device CL2 and the second inner support member 54 etc. However, the annular member 10 fixed to the inner periphery of the cylindrical portion 21 abuts against the first pressing portion 422 of the first piston portion 42 from above, restricting further downward movement of the rotor support member 2 etc. This restricts the first outer friction material 412 from moving relatively upward beyond the opening on the axial first side L1 of the rotor support member 2. Therefore, the spline engagement between the first outer friction material 412 and the cylindrical portion 21 is released, and the rotor support member 2 etc. can be restricted from falling off. In other words, this structure is capable of restricting a part of the first assembly AS1 from falling off through the opening of the rotor support member 2.

In addition, since the above formula (1) is satisfied at this time, even if the axial center positions of the input member I and the rotor support member 2 are misaligned and the outer periphery of the first piston portion 42 comes into contact with the inner periphery of the cylindrical portion 21, the annular member 10 can maintain a state in which it overlaps with the first piston portion 42 when viewed in the axial direction. Therefore, the structure can reliably prevent a part of the first assembly AS1 from falling off through the opening of the rotor support member 2.

At this time, the second outer support member 55 supporting the second outer friction material 512 moves downward together with the second inner support member 54 due to the weight of the second engagement device CL2, etc. However, further downward movement of the second outer support member 55 is restricted by the flange portion 22. In addition, downward movement of the second piston portion 52 is also restricted by the flange portion 22.

The first side wall portion 11 to which the stator St, the first bearing B1, and the third bearing B3 are attached is assembled to the first assembly AS1. This assembly work may be performed either before or after the first assembly AS1 is assembled to the second assembly AS2.

Other embodiments
(1) In the above embodiment, a configuration has been described as an example in which the first outer support member 48 is formed integrally with the cylindrical portion 21. However, the present invention is not limited to such a configuration, and the first outer support member 48, like the second outer support member 55, may be a separate member independent of the cylindrical portion 21.

(2) In the above embodiment, a configuration has been described in which the rotor cooling holes 21b as the first supply holes are formed to open to the outer periphery of the cylindrical portion 21 on the second axial side L2 relative to the protrusion 21a. However, the present invention is not limited to such a configuration, and for example, the rotor cooling holes 21b may be formed to open to the outer periphery of the cylindrical portion 21 on the first axial side L1 relative to the protrusion 21a. Alternatively, a configuration may be used in which the rotor cooling holes 21b are not provided.

(3) In the above embodiment, the gap G between the outer peripheral surface of the cylindrical portion 21 and the inner peripheral surface of the rotor core Roc functions as an oil passage for cooling the rotor Ro, but the present invention is not limited to such a configuration. The oil passage for cooling the rotor Ro may be formed in any one of the rotor support member 2, the holding member H, and the rotor Ro, or in the gap at the boundary between these. For example, the oil passage for cooling the rotor Ro may be formed in the gap at the boundary between the holding member H and the rotor Ro.

(4) In the above embodiment, a configuration has been described as an example in which a supply part SP is provided that supplies oil to the inner periphery of the first inner support member 44 from the radial inside R1, and the first communication hole 44a is formed as a second supply hole that penetrates the first inner support member 44 in the radial direction R. However, the present invention is not limited to such a configuration, and for example, a configuration in which the first communication hole 44a is not formed and oil is supplied to the first friction member 41 from a direction other than the radial inside R1 may be used. Alternatively, a configuration without a supply part SP may be used.

(5) In the above embodiment, a configuration in which the second engagement device CL2 is disposed adjacent to the first engagement device CL1 on the second axial side L2 has been described as an example. However, the present invention is not limited to such a configuration, and may be configured, for example, in which the second engagement device CL2 is disposed at a position shifted in the radial direction R from the first engagement device CL1. Alternatively, a configuration in which the second engagement device CL2 is not provided may also be used.

(6) In the above embodiment, when the first assembly AS1 and the second assembly AS2 are assembled, the input member I is held so that the second engagement device CL2 is positioned lower than the first engagement device CL1. However, without being limited to such a method, when the first assembly AS1 and the second assembly AS2 are assembled, the rotor support member 2 may be held so that the second engagement device CL2 is positioned higher than the first engagement device CL1. In this case, the first pressing portion 422 of the first piston portion 42 abuts against the annular member 10 from above, thereby restricting further downward movement of the first engagement device CL1 and the input member I, etc. Therefore, even with this method, it is possible to prevent a part of the first assembly AS1 from falling off through the opening of the rotor support member 2.

(7) In the above embodiment, the power transmission mechanism T is a transmission TM that has multiple gear stages with different gear ratios and changes the rotation transmitted from the rotating electric machine MG at a gear ratio corresponding to the formed gear stage. However, the power transmission mechanism T is not limited to such a configuration, and may be, for example, a fixed gear ratio transmission (reduction gear or speed increaser) that changes the rotation transmitted from the rotating electric machine MG at a constant gear ratio. Alternatively, the power transmission mechanism T may be configured to transmit the rotation transmitted from the rotating electric machine MG to the transmission output gear G1 at the same rotational speed.

(8) In the above embodiment, the vehicle drive device 100 is configured as a drive device for a hybrid vehicle of a one-motor parallel system. However, the present invention is not limited to such a configuration. The vehicle drive device 100 may be a drive device for a hybrid vehicle of a so-called series-parallel system, which includes an internal combustion engine EG and two rotating electric machines, or may be a drive device for a hybrid vehicle of a so-called split system, which includes an internal combustion engine EG, two rotating electric machines, and a differential gear mechanism (e.g., a planetary gear mechanism) for power distribution, and which distributes the driving force of the internal combustion engine EG to a first rotating electric machine that mainly functions as a generator and a second rotating electric machine that mainly functions as a wheel and an electric motor.

(9) The configurations disclosed in each of the above-described embodiments may be combined with configurations disclosed in other embodiments, provided no contradictions arise. With respect to other configurations, the embodiments disclosed in this specification are merely examples in all respects. Therefore, various modifications may be made as appropriate within the scope of the spirit of this disclosure.

[Summary of the above embodiment]
The following provides an overview of the vehicle drive device (100) described above.

The vehicle drive device (100) includes:
an input member (I) drivingly connected to an internal combustion engine (EG);
a rotating electric machine (MG) having a stator (St) and a rotor (Ro) arranged on the inside (R1) of the stator (St) in a radial direction (R), and functioning as a driving force source for wheels (W);
a power transmission mechanism (T) that transmits rotation transmitted from the rotating electric machine (MG) to the wheels;
A rotor support member (2) that supports the rotor (Ro);
a first engagement device (CL1) having a first friction plate (412) and a second friction plate (411) arranged side by side in an axial direction (L), and a first piston portion (42) that presses the first friction plate (412) and the second friction plate (411) in the axial direction (L),
The first engagement device (CL1) is disposed in a power transmission path between the input member (I) and the rotating electric machine (MG),
A first outer support member (48) that supports the first friction plate (412) from the outer side (R2) in the radial direction (R);
A first inner support member (44) that supports the second friction plate (411) from the inner side (R1) in the radial direction (R),
The first inner support member (44) includes a cylindrical support portion (441) that is formed in a cylindrical shape extending along the axial direction (L) and supports the second friction plate (411), and a radially extending support portion (442) that is formed so as to extend from the cylindrical support portion (441) to an inner side (R1) in the radial direction (R),
the radially extending support portion (442) is coupled to the input member (I) such that the input member (I) and the first inner support member (44) rotate together;
The first piston portion (42) is disposed on a first axial side (L1) that is one side of the axial direction (L) with respect to the radially extending support portion (442),
The rotor support member (2) includes a cylindrical portion (21) formed in a cylindrical shape extending along the axial direction (L) and supporting the rotor (Ro) from an inner side (R1) of the radial direction (R), and a flange portion (22) formed to extend along the radial direction (R) on the inner side (R1) of the radial direction (R) relative to the cylindrical portion (21) and connected to the cylindrical portion (21);
the first engagement device (CL1) is disposed on the first axial side (L1) with respect to the flange portion (22) and on the inner side (R1) in the radial direction (R) with respect to the cylindrical portion (21);
The first outer support member (48) is configured to open toward the first axial side (L1) and rotate integrally with the cylindrical portion (21),
An annular member (10) formed in an annular shape extending along a circumferential direction is fixed to an inner peripheral portion of the cylindrical portion (21),
The annular member (10) is located on the first axial side (L1) with respect to the first friction plate (412) and the second friction plate (411), and is positioned so as to overlap with at least one of the first piston portion (42) and the second friction plate (411) when viewed in the axial direction along the axial direction (L).

According to this configuration, when the first assembly (AS1) including the rotor (Ro), the rotor support member (2), and the first engagement device (CL1) is assembled to the second assembly (AS2) separate from the first assembly (AS1), even if the first engagement device (CL1) moves relative to the rotor support member (2) toward the first axial side (L1), at least one of the first piston portion (42) and the second friction plate (411) abuts against the annular member (10). This makes it possible to restrict the first friction plate (412) of the first engagement device (CL1) from moving relative to the opening on the first axial side (L1) of the rotor support member (2) toward the first axial side (L1). In other words, it is possible to restrict the first friction plate (412) from coming off the rotor support member (2). Therefore, when a first assembly (AS1) including a rotor (Ro), a rotor support member (2), and a first engagement device (CL1) is assembled to a second assembly (AS2) separate from the first assembly (AS1), the structure is capable of preventing a part of the first assembly (AS1) from falling off through the opening in the rotor support member (2).

Here, the diameter of the inner peripheral surface of the cylindrical portion (21) is D1,
The outermost diameter of the first piston portion (42) is D2,
A distance in the radial direction (R) from an inner peripheral surface of the cylindrical portion (21) to an inner peripheral end of the annular member (10) is defined as D3,
D1-D2 <D3
It is preferable that:

According to this configuration, even if the input member (I) becomes eccentric and the outer periphery of the first piston portion (42) comes into contact with the inner periphery of the cylindrical portion (21), the annular member (10) can maintain a state where it overlaps with the first piston portion (42) when viewed in the axial direction. This can reliably prevent a part of the first assembly (AS1) from falling off through the opening of the rotor support member (2) when assembling the first assembly (AS1) to the second assembly (AS2).

Further, a first supply hole (21b) communicating with an oil passage (G) for cooling the rotor (Ro) is formed in the cylindrical portion (21),
It is preferable that the first supply hole (21b) is formed so as to open to the inner peripheral portion of the tubular portion (21) on a second axial side (L2) opposite the first axial side (L1) with respect to the annular member (10).

According to this configuration, the oil supplied to the inner periphery of the cylindrical portion (21) is restricted from flowing toward the first axial side (L1) by the annular member (10), so that a large amount of oil can be supplied to the first supply hole (21b). This allows the rotor (Ro) to be efficiently cooled through the first supply hole (21b).

The oil supply unit (SP) supplies oil to the inner periphery of the first inner support member (44) from the inside (R1) in the radial direction (R),
It is preferable that a second supply hole (44a) is formed in the first inner support member (44) so as to penetrate the first inner support member (44) in the radial direction (R).

According to this configuration, by utilizing the centrifugal force of a rotating member such as the rotor support member (2) provided in the vehicle drive device (100), oil can be appropriately supplied from the inside (R1) in the radial direction (R) to the inner peripheral portion of the first inner support member (44). Then, the oil supplied to the inner peripheral portion of the first inner support member (44) can be supplied to the second friction plate (411) through the second supply hole (44a). Therefore, the pair of the first friction plate (412) and the second friction plate (411) can be appropriately lubricated and cooled.

a second engagement device (CL2) including a third friction plate (512) and a fourth friction plate (511) arranged side by side in the axial direction (L), and a second piston portion (52) that presses the third friction plate (512) and the fourth friction plate (511) in the axial direction (L);
A second outer support member (55) that supports the third friction plate (512) from the outer side (R2) in the radial direction (R);
A second inner support member (54) that supports the fourth friction plate (511) from the inner side (R1) in the radial direction (R),
The second engagement device (CL2) is disposed adjacent to the first engagement device (CL1) on an axial second side (L2) that is opposite to the axial first side (L1),
The second outer support member (55) is configured to rotate integrally with the rotor support member (2),
It is preferable that the second piston portion (52) is supported so as to rotate integrally with the rotor support member (2).

According to this configuration, the flange portion (22) is disposed on the second axial side (L2) relative to the second engagement device (CL2). This allows the flange portion (22) to restrict movement of the second engagement device (CL2) toward the second axial side (L2). Therefore, when a first assembly (AS1) in which the rotor (Ro), rotor support member (2), first engagement device (CL1), and second engagement device (CL2) are integrally assembled is assembled to a second assembly (AS2) separate from the first assembly (AS1), the opening of the rotor support member (2) faces upward, thereby restricting the second engagement device (CL2) from falling off the rotor support member (2).

In the configuration including the second engagement device (CL2),
It is preferable that the flange portion extends radially inward beyond the second engagement device.

This configuration makes it possible to highly reliably prevent the second engagement device (CL2) from falling off the rotor support member (2) when the first assembly (AS1) is assembled to the second assembly (AS2) with the opening of the rotor support member (2) facing upward.

It is also preferable that the second engagement device (CL2) is disposed in the power transmission path between the rotating electric machine (MG) and the power transmission mechanism (T).

According to this configuration, by switching the engagement state between the first engagement device (CL1) and the second engagement device (CL2), it is possible to switch between a state in which only the rotating electric machine (MG) of the rotating electric machine (MG) and the internal combustion engine (EG) is connected to the power transmission mechanism (T), a state in which both the rotating electric machine (MG) and the internal combustion engine (EG) are connected to the power transmission mechanism (T), and a state in which the rotating electric machine (MG) and the internal combustion engine (EG) are connected and separated from the power transmission mechanism (T).

It is also preferable that the power transmission mechanism (T) is a transmission (TM) that has multiple gear stages with different gear ratios and changes the rotation transmitted from the rotating electric machine (MG) at a gear ratio corresponding to the formed gear stage.

With this configuration, the driving force transmitted to the wheels (W) can be changed as needed.

The technology disclosed herein can be used in a vehicle drive device that includes a rotating electric machine that has an input member that is drivingly connected to an internal combustion engine, a stator, and a rotor that is arranged radially inward of the stator and functions as a driving force source for the wheels, a power transmission mechanism that transmits the rotation transmitted from the rotating electric machine to the wheels, a rotor support member that supports the rotor, and a friction engagement device.

100: Vehicle drive device 2: Rotor support member 21: Cylindrical portion 22: Flange portion CL1: First engagement device 411: First inner friction material (second friction plate)
412: First outer friction material (first friction plate)
42: First piston portion 44: First inner support member 441: First cylindrical support portion (cylindrical support portion)
442: First radial extending portion (radial extending support portion)
48: First outer support member 10: Annular member MG: Rotating electric machine St: Stator Ro: Rotor T: Power transmission mechanism W: Wheel L: Axial direction L1: Axial first side L2: Axial second side R: Radial direction R1: Radial inner side R2: Radial outer side

Claims (8)

an input member drivingly connected to the internal combustion engine;
a rotating electric machine having a stator and a rotor disposed radially inward of the stator and functioning as a driving force source for a wheel;
a power transmission mechanism that transmits rotation transmitted from the rotating electric machine to the wheels;
a rotor support member for supporting the rotor;
a first engagement device including a first friction plate and a second friction plate arranged side by side in the axial direction, and a first piston portion that presses the first friction plate and the second friction plate in the axial direction,
The first engagement device is disposed in a power transmission path between the input member and the rotating electric machine.
a first outer support member that supports the first friction plate from an outer side in the radial direction;
A first inner support member that supports the second friction plate from the inside in the radial direction,
the first inner support member includes a cylindrical support portion that is formed in a cylindrical shape extending along the axial direction and supports the second friction plate, and a radially extending support portion that is formed so as to extend radially inward from the cylindrical support portion,
the radially extending support portion is coupled to the input member such that the input member and the first inner support member rotate together;
The first piston portion is disposed on a first axial side, which is one side in the axial direction, with respect to the radially extending support portion,
the rotor support member includes a cylindrical portion formed in a cylindrical shape extending along the axial direction and supporting the rotor from the inside in the radial direction, and a flange portion formed in a radially inner side relative to the cylindrical portion and extending along the radial direction and connected to the cylindrical portion,
The first engagement device is disposed on a first side in the axial direction with respect to the flange portion and on an inner side in the radial direction with respect to the cylindrical portion,
the first outer support member is configured to open toward the first axial side and rotate integrally with the cylindrical portion,
An annular member is fixed to an inner peripheral portion of the cylindrical portion and extends in a circumferential direction.
the annular member is disposed on the first axial side with respect to the first friction plate and the second friction plate, and at a position overlapping with at least one of the first piston portion and the second friction plate as viewed in the axial direction along the axial direction,
the first piston portion abuts against the second friction plate from the first axial side on an axial second side opposite the first axial side with respect to the annular member, thereby pressing the first friction plate and the second friction plate in the axial direction. The diameter of the inner circumferential surface of the cylindrical portion is D1,
The outermost diameter of the first piston portion is D2,
The radial distance from the inner circumferential surface of the cylindrical portion to the inner circumferential end of the annular member is defined as D3,
D1-D2 <D3
2. The vehicle drive device according to claim 1, wherein: a first supply hole communicating with an oil passage for cooling the rotor is formed in the cylindrical portion;
The vehicle drive device according to claim 1 , wherein the first supply hole is formed so as to open to an inner periphery of the cylindrical portion on the second axial side with respect to the annular member. a supply unit that supplies oil to an inner circumferential portion of the first inner support member from an inner side in the radial direction,
The vehicle drive device according to claim 1 , wherein a second supply hole is formed in the first inner support member so as to penetrate the first inner support member in the radial direction. a second engagement device including a third friction plate and a fourth friction plate arranged next to each other in the axial direction, and a second piston portion that presses the third friction plate and the fourth friction plate in the axial direction;
a second outer support member that supports the third friction plate from the outside in the radial direction;
A second inner support member that supports the fourth friction plate from the inside in the radial direction,
The second engagement device is disposed adjacent to the first engagement device on the second axial side,
the second outer support member is configured to rotate integrally with the rotor support member;
The vehicle drive device according to claim 1 , wherein the second piston portion is supported so as to rotate integrally with the rotor support member. The vehicle drive device according to claim 5, wherein the flange portion extends radially inward beyond the second engagement device. The vehicle drive device according to claim 5 or 6, wherein the second engagement device is disposed in a power transmission path between the rotating electric machine and the power transmission mechanism. The vehicle drive device according to any one of claims 1 to 7, wherein the power transmission mechanism is a transmission that has a plurality of gear stages with different gear ratios and changes the rotation transmitted from the rotating electric machine at a gear ratio corresponding to the formed gear stage.

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